Rotary-type hydraulic machine

ABSTRACT

The present invention relates, preferably, the transport machinery, and more particularly it relates to the rotary-type hydraulic machines, used, particularly, in power transmissions of locomotives, tractors, tracks, transport vehicles as well as in the drives of machine tools and other machines.

United States Patent [72] Inventors Alexandr lvanovieh Kravlsov ulitsa Engelsa obschezhite lGlhKomnata 28, Ljudinovo, Kaluzhskoi, Oblasti; Viktor Viktorovich Domogalsky, ulitsa Molodezhnaya 6, kv. 60, Ljudinovo, Kaluzhsltoi, Oblasti; Sergei Kazimirovich Rushat, ulitsa Semasllko, 5, kv. 6, Ljudinovo, Kaluzhskoi, Oblmti; Pavel Nikilovich Mazurov, ulitsa Leuina, 16/9, Irv. 6, Ljudinovo, Kaluzhskoi, Ohlasti; Vasily Petmvich Kopantsov, ulitsa Vostochnaya, 26-a, kv. 44, Kremenchug; Vladimir Grigorievich Lavrukhin, ulitsa Lenina, 7 kv. l2, Ljudinovo, Kaluzhskoi, Oblasti; Viktor Vladimirovich Gordeev, ulitsa Lenina, 3, kv. 24, Ljudinovo, Kaluzhskoi, Oblasti; Eedor Anpalievich Dimitriev, ulitsa Kosmonavtov, 6, kv. 8,

Primary ExaminerWilliam L. Freeh AssLrtan! Examiner-Wilbur .1. Goodlin AttarneyWaters, Roditi, Schwartz & Nissen Moscow, all of, U.S.S.R. [21] Appl. No. 850,565 [22] Filed Aug. 15, 1969 [45] Patented Aug. 3, 1971 ABSTRACT: The present invention relates, preferably, the transport machinery, and more particularly it relates to the ro- [54] HYDRULIC MACHINE tary-type hydraulic machines, used, particularly, in power buns rawmg transmissions of locomotives, tractors, tracks, transport vehi- [52] U.S.Cl 418/20, cles as well as in the drives of machine tools and other 418/191,418/l96 machines.

77 30 1/0626/54 27:5 5/ J6 5 x s, 25

5 9 5 I m 57 H 3] F N "L Patented Aug. 3, 1971 3,597,127

5 Sheets-Sheet 1 FIGI Patented Aug. 3, 1971 5 Sheets-Sheet 2 m 3 NW MN m llhLll/L Patented Aug. 3, 1971 3,597,127

5 Sheets-Sheet 5 FIG. 5

FIGJ

Patented A 3 19 5 Sheets-Sheet 4 Patented Aug. 3, 1971 3,597,127

5 Sheets-Sheet 5 FIG] ROTARY-TYPE HYDRAULIC MACHINE The present invention relates preferably to the field of transport machinery, and more particularly it relates to rotarytype hydraulic machines, used, particularly, in power transmissions for diesel engine locomotives, tractors, automatic loaders, vehicles, as well as in the drives of machine tools and other machines.

Known in the prior art are rotary type hydraulic machines for the drives, particularly of transport vehicles, wherein a vane-type rotor installed on the shaft in the casing, and at least one rotating locking member, connected to said rotor and having a cutout for the vanes to pass through, together with the control member form at least two variable volume chambers (Federal Republic of Germany Pat. No. l,2l5,532, Cl. 63c-360l The known rotary-type hydraulic machines have the following disadvantages.

The chamber capacity in the known rotary-type hydraulic machines is usually controlled by a central slide valve distribu tor, which disengages one or several rotor vanes, that is, a stepped control of the chamber capacity is ensured, which is undesirable, as it causes the rotor disbalance, the working fluid pulsation and hydromechanical losses in the course of the rotary-type hydraulic machine operation with the vanes disengaged, and does not ensure smooth variation of the traction characteristics.

Said disadvantages limit the field of application of the known hydraulic machines for the operation at high pressures ofthe working fluid and at high values of the rotor r.p.m.

An object of the present invention is to provide a rotarytype hydraulic machine for the drives, preferably of transport vehicles, simple in design and reliable in operation, which would ensure smooth control of the chamber capacity and consequently smooth variation of the traction forces within a wide range of the rotor rpm. and at high pressures of the working fluid.

This object is achieved by that in a rotary-type hydraulic machine for the drives, preferably of transport vehicles, according to the invention, the rotor and the control member intended for forming variable capacity chambers, are installed in the casing, a possibility being provided for their reciprocation in the axial direction relative to the rotatable locking members and a bushing, installed inside the front part of the casing and having grooves in its front part to allow the rotor vanes to pass through.

it is expedient to employ a power means for ensuring reciprocating movement of the rotor with the control member, said power means being fashioned as a hydraulic cylinder whose internal cavity is formed by the internal surfaces of the casing rear part and the face parts of the rotor and control member, said cavity communicating with the fluid supply means through a hole in the casing.

It is also expedient to make the control member in the form of a shaped bushing, installed on the rotor hub by means of bushings and provided with four longitudinal semicylindrical bores on its external surface, locking members being placed in said bores.

The bushing having grooves, installed inside the casing front portion, can be mounted on the hollow member, connected to the base, by means ofa rolling friction bearing.

The bushing having grooves, installed inside the casing front part, can also by mounted on the rotor hub, bearing upon the hollow member, connected to the hydraulic machine casing.

It is expedient to install the locking members in such a manner that their shafts, connected to the hydraulic machine shaft, be cantilevered in the rear part of the casing by means of bearings and to locate them in the four longitudinal semicylindrical bores along the internal surface of the casing, said bores being matched with the four semicylindrical longitudinal bores along the external surface of the shaped bushing.

It is expedient, that each locking member be provided with a hole in the cutout for the rotor vanes passing through, said hole should periodically connect the variable capacity chamber with the clearance between the rear working portion of the locking member and bearing for the axial relief of the locking member by the pressurized working fluid.

It is desirable, that crescent-shaped recesses be provided in the casing above the operating parts of the locking members, said recesses periodically communicating with the variable capacity chambers to ensure radial relief of the locking members by the pressure of the working fluid.

it is desirable, that each locking member be provided with a longitudinal channel which would connect the cutout through a drilled hole with a circular groove, made on the rear face of said shaft to ensure the axial relief of the locking member by the pressurized working fluid.

It is expedient to provide several crescent-shaped recesses along the length of the cutouts in the locking members on the control member, under the operating parts of the locking members and to provide shears of the edges in the semicylindrical bores of the casing intended for the locking members, said shears being also located along the length of the cutouts, and periodically communicating all said recesses or a certain portion thereof with the variable volume chambers to ensure constant pressure of the working fluid onto the operating part of the locking members, when the volume of said chambers is being varied.

It is expedient to provide recesses in the semicylindrical bores of the casing above the locking member shafts in their front part, and under the shafts in their rear part, said recesses would periodically communicate with the variable volume chambers for the radial relief of the locking members through grooves, vertical and longitudinal passages, made in the casmg.

ln the front upper part of the shafts and in the rear lower part thereof it is also expedient to provide recesses, which would communicate periodically through the vertical and iongitudinal channels, made in the shafts of the locking members, with the variable volume chambers to ensure the radial relief of the locking members. It is desirable, that the shaped bushing be provided with a longitudinal passage, through which the variable volume chambers would communicate with a circular groove, closed by a bearing flange, said groove being made on the rear face part of said bushing to ensure its axial relief by the pressurized working fluid.

The longitudinal channel in the shaped bushing can communicate with the circular groove made on the surface of the bearing flange, which contacts with said bushing.

It is expedient to have grooves which are located between the semicylindrical bores for the locking members and which are somewhat narrower than the width of the rotor vanes, said grooves would communicate periodically with the variable volume working chamber to ensure the radial relief of the rotor by the pressurized working fluid.

It is expedient, that the bushing, having grooves, for the rotor blades to pass through, be provided with two diametrically opposite longitudinal passages, through which the variable volume chambers communicate with the circular groove, made on the base to balance the axial hydrostatic forces, occurring between the rotor, control member and said bushing.

Other objects and advantages of the present invention will become apparent by analyzing the description of the invention with reference to the appended drawings, wherein:

FIG. 1 shows a perspective view of a rotary-type hydraulic machine, according to the present invention, a disassembled state;

FIG. 2 is a side view (a section, takenalong the line ll-ll of FIG. 3) of the rotary-type hydraulic machine, wherein, according to the present invention, a control member is installed by means of bearings on the rotor hub, a bushing, provided with grooves, is installed in the same way on the hollow member, connected to the machine casing, and locking members are installed in the same manner, their shafts being cantilevered in the rear part of the casing;

FIG. 3 shows a front view of the same (a section being taken along the line III-III of FIG. 2);

FIG. 4 shows a side view (a section, taken along the line lV-IV of FIG. 5 of an embodiment of the rotary-type hydraulic machine, wherein, according to the invention, a bushing having grooves, is mounted on the rotor hub, bearing upon a hollow member;

FIG. 5 shows a front view ofthe same (a section being taken along the line V-V of FIG. 4);

FIG. 6 shows elements for the radial and axial relief of the locking members, a section being taken along the line VI-VI of FIG. 5;

FIG. 7 shows a development of the internal surface of the bore in the rear part of the casing for the locking member;

FIG. 8 shows elements, ensuring constant pressure of the working fluid, acting on the working part of the locking mem bers, when the chamber capacity is being changed; a section being taken along line VIII-VIII of FIG. 6;

FIG. 9 shows a development of a part of the surface of the control member in the bore for the locking member;

FIG. 10 shows element in the front part of the locking members for their radial relief in the course of the working fluid forcing prior to communicating the variable volume chambers with the cutouts in said locking members, a section being taken along the line IX-IX of FIG. 6;

FIG. 11 shows elements in the rear part of the locking members for their radial relief in the course of the working fluid forcing prior to communicating the variable volume chambers with the cutouts in said locking members, a section being taken along the line X-X of FIG. 6.

When describing the present embodiment of the invention concrete terms are used for the sake of clarity. However, it should be borne in mind, that the invention is not restricted by the narrow terms so selected and that each of these terms embraces all the equivalent elements, operating in the same manner and used for solving the same problems.

The rotary-type hydraulic machine comprises a casing consisting of a front part I FIGS. 1, 5) and a rear part 2, a shaft 3, accommodated in said casing; a rotor 4 with two vanes 5, said rotor being installed on said shaft inside said casing, according to the invention, a possibility being provided for said rotor to reciprocate axially; a power means 6 (FIGS. 2 and 7) to ensure the reciprocating motion of said rotor; a control member 7, installed in the rear part2 of the casing and according to the invention, movable together with said rotor, as well as interacting with said'power means; a bushing 8 installed inside the front part 1 of said casing and having grooves 9 in its face part for the vanes 5 of said rotor to move; four rotatable locking members 10 with cutouts 11 for the rotor vanes to pass through and four variable volume chambers 12 (FIGS. 3, 5 formed by said movable rotor and control member relative to said locking members and bushing, as well as by said locking members and bushing.

The front part 1 of the casing has a circular space 13 (FIG. 2) and passages 14.

The rear part 2 of the casing has four longitudinal semicylindrical bores 15 (FIG. 1) along the internal surface thereof.

In the rear part 2 of the casing between said semicylindrical bores there are recesses 16 (FIGS. 3, 5), which are, according to the invention, somewhat narrower, than the width of the vanes 5 of the rotor 4, said recesses periodically communicating with the variable volume working chambers 12 during the hydraulic machine operation to ensure radial relief of said rotor 4 by the pressurized working fluid.

The shaft 3 is installed in the hydraulic machine casing with the help ofbearings l7 and 28 (FIGS. 2 and 4).

The rotor 4 has passages 19 (FIGS. 3 and 5), communicating the variable volume working chambers 12 with the fluid inlet system, and holes 20 in the vanes 5 of said rotor, said holes communicating with the outlet fluid system.

The power means 6 (FIGS. 2 and 4) ensuring the reciprocating movement of the rotor 4 with the control member 7 is made as a hydraulic cylinder, according to the invention, the space 21 of said hydraulic cylinder is formed by the internal surfaces of the casing rear part 2 and the face parts of the rotor 4 and control member 7 and communicates through the hole 22 in the casing with the working fluid supply means (not shown in the drawing).

The control member 7 according to the invention, is made as a shaped bushing with four longitudinal semicylindrical bores 23 (FIG. 1) along its external surface.

Said shaped bushing is installed on the hub 24 (FIGS. 2, 4) of the rotor 4.

Located in the bores 23 of the shaped bushing are locking members 10.

The bushing 8 having grooves 9 is mounted on the hollow member 25, connected to a plate 26, according to the invention.

According to the invention, the locking member 10 by their shafts 27 are cantilevered in the rear part 2 of the casing. They are located in the four longitudinal semicylindrical bores 15 along the internal surface of the rear part 2 of the casing. Said bores coincide with the four longitudinal semicylindrical bores 23 along the external surface of the shaped bushing. The shafts 27 of the locking members 10 are connected to the shaft 3 by means ofgears 28 and 29 (FIGS. 1, 2, 4).

According to the invention, given below are two design embodiments of the invention.

The first embodiment (FIGS. 1, 2, 3) of the rotary-type hydraulic machine.

A plate 26 having holes 31 and 32 is attached by screws 30 (FIG. 2) to the front part 1 of the casing, some of said holes 31 communicate with the circular space of the hollow member 25, while the others 32 with the passages 14.

The end of the shaft 3 and a cup seal 33 are installed in said plate with the help of a rolling friction bearing 17. A circular collector 34 is secured to the plate 26, said collector having an inlet pipe union 35 and an outlet pipe union 36 coinciding with the respective holes 31 and 32 of the plate 26. Secured to the rear part 2 of the casing is a cover 37 with a flange 38, in which a cup seal 39 is installed.

The rotor 4 with the hub 24 is loosely installed on the shaft 3 with the help of splines 40.

In order to ensure reciprocating movement of the rotor 4 in the described embodiment a screw 41, connected to the control member 7, can be used. A lever 42, installed in a hole 43, is used for feedback connection with the control slide valve (not shown in drawing).

The control member 7, fashioned as a shaped bushing, is installed on the hub 24 with the help of rolling friction bearings 44 and 45, and a bearing flange 46 with a nut 47 prevents the axial displacements of said member 7. Distance bushings 48 and 49, a circular projection 50 in the shaped bushing and a stop nut 51 prevent the rolling friction bearings 45 from axial displacements.

The shaped bushing according to the invention, has a longitudinal passage 52, by means of which the variable volume chambers 12 communicate with a circular recess 53, closed by the bearing flange 46, said recess being made on the rear face part of said bushing for its axial relief by the pressurized working fluid.

The locking members 10 are installed by their shafts 27 in the rear part 2 of the casing by means of the rolling friction bearings 54 and 55, whose axial displacement is prevented by distance bushings 56 and 57 and bearing flanges 58. The gears 28 and 29 are secured in the rear part of the shafts 27 of the locking members 10 by means of screws 59.

The locking members 10 are located by their shafts 27 in the four longitudinal semicylindrical bores 15 along the internal surface of the rear part 2 of the casing, said bores being matched with the four longitudinal semicylindrical bores 23 along the external surface of the shaped bushing.

In order to ensure axial relief of the locking members 10, according to the invention, each of said locking members has a hole 60 (FIGS. 1 and 3) in the cutout 11 for the vanes 5 of the rotor 4 to pass through, the pressurized working fluid of the variable volume chambers 12 communicating periodically through said hole 60 with a clearance 61 (FIG. 2) between the rear part of the locking member and the rolling friction bearing 54.

In order to ensure the radial relief of the locking members 10, according to the invention, crescent-shaped recesses 62 are provided in the rear part2 of the casing above the working parts of the locking members 10, said recesses communicating periodically with the pressurized working fluid of the variable volume chambers 12.

The bushing 8 having grooves 9 and mounted inside the front part 1 ofthe casing on the hollow member 25, is installed by means of a rolling friction bearing 63 (FIG. 2). The hollow member 25 is connected to the plate 26 with the help of screws 64, the circular space 65 of said hollow member communicating with the variable volume chamber 12 through the channels 19 in the vanes 5 of the rotor 4. The bearing 63 is fixed on the hollow member 25 by a ring 65 connected by said bushing by means of screws 66 and a nut 67.

The bushing 8 having the grooves 9 for the rotor vanes to move according to the invention, is provided with two diametrically opposite longitudinal channels 68, which communicate the variable volume chambers 1 with the circular recess 69, made on the plate 26 to balance the axial hydrostatic forces, occurring between the rotor 4, control member 7 and said bushing.

The rotary-type hydraulic machine functioning as a pump, according to the present invention, operates as follows:

When the shaft 3 rotates in the clockwise direction, the rotor 4 with the vanes 5 as well as all the four locking members 10, connected to said shaft by means of the gears 28 and 29 also rotate. The vanes 5 of the rotor 4 are located in the grooves 9 of the bushing 8, owing to which said bushing also rotates. Simultaneously the fluid is sucked into the pipe union 35, wherefrom it is delivered into the hole 31 in the plate 26, and farther into the circular space of the hollow member 25, whence the fluid is delivered along the passages 19 in the rotor 4 into the two diametrically opposite variable volume chambers 12, communicating directly with the passages 19. The fluid contained in the two other diametrically opposite variable volume chambers 12, is forced from them by the vanes 5 through the holes in the vanes 4 of the rotor 5 and is delivered through the grooves 9 and holes 70 (FIG. 1) in the bushing S into the circular space 13. Then through the passages 14 in the front part 1 of the casing and the holes 32 in the plate 26 the fluid is forced out through the outlet pipe union 36 of the circular collector 34 into the delivery pipeline.

The fluid consumption is varied by moving the rotor 4 along the shaft 3 by means of the power means 6. In this case in order to reduce the consumption of the fluid the pressurized fluid is delivered into the space 21 of the power means 6 through the hole 22 in the rear part 2 of the casing with the help of a means adapted for its delivery. In this case the fluid forced into the space 21 acts on the rear face part of the shaped bushing and on the bearing flange 46 and moves them to the left (according the the drawing) axially along the shaft 3. Consequently, the rotor 4 will move together with said bushing and flange and will enter by its vanes 5 the grooves 9 of the bushing 8, due to which the volume of the variable volume chambers 12, formed between said rotor, locking members 10, control member 7 and the bushing 8 will be reduced.

In order to increase the fluid consumption in the space 21 of the power means 6 the pressure of the fluid is reduced with the help of the means for its delivery. In this case the pressure of the working fluid in the variable volume chambers 12 acts on the vanes 5 of the rotor 4 and on the control member 7, which are moved backward, therefore the volume of said chambers 12 will be increased, and, consequently, the working fluid consumption will be increased.

The working fluid consumption can also be varied with the help of screw 41, connected to the shaped bushing.

During the hydraulic machine operation, the holes 60 in the cutouts 11 of the locking members 10 periodically communicate with the variable volume chambers 12, which fact ensures the axial relief of the locking members, owing to the delivery of the pressurized working fluid into the clearances 61 between the rear working parts of the locking members 10 and the rolling friction bearings 54.

The crescent-shaped recesses 62 also communicate periodically with the chambers 12, which ensures the radial relief of the locking members owing to the delivery of the pressurized working fluid into said recesses. The circular recess 69 communicates with the chambers 12 through two diametrically opposite passages 68, which ensures the balance of the axial hydrostatic forces, occurring between the rotor 4, control member 7 and bushing 8.

The rotary-type hydraulic machine can be used as a hydraulic motor. This is achieved by delivering pressurized fluid into the pipe union 36 of the collector 34.

The second embodiment of the rotary-type hydraulic machine (FIGS. 4 to 1 l).

The front part 1 (FIG. 4) of the casing is provided with an outlet 71, while the plate 26-with an inlet 72-communicating with the circular space of the hollow member 25.

The plate 26 and the front part 1 of the casing are connected to the rear part 2 by means of bolts 73. The hollow member 25 is installed on the shaft 3 by means of the bearing 17 and flange 74 and is fastened to the plate 26 by means of bolts 75.

The rotor 4 is installed on the shaft 3 by means of a key 76 in such a way that the reciprocating motion of said rotor along said shaft is provided.

The control member 7, fashioned as a shaped bushing, is installed directly on the hub 24 of the rotor 4, held thereon with the help of the bearing flange 46 and nut 47, and is provided with a rolling friction bearing 77. The longitudinal passage 52 in the shaped bushing communicates the variable volume chambers 12 (FIG. 5) with the circular recess 53, made, according to the invention, on the surface of the bearing flange 46, contacting with said bushing.

Located in the shaped bushing under the working parts of the locking members 10, according to the invention, are several crescent-shaped recesses 78 (FIGS. 4, 6, 9), arranged along the length of the cutouts 11 of the locking members 10, and in the semicylindrical .bores 15 of the rear part 2 of the casing there are shears 79 (FIG. 8) of the edges for said locking members, said shears being also located along the length of said cutouts 11, all the crescent-shaped recesses or a certain part thereof periodically communicating with the variable volume chambers 12 through said shears, which ensures constant pressure of the working fluid, acting on the working part of the locking members 10 as the working volume of said chambers is varied.

Located in the semicylindrical bores 15 of the casing above the shafts 26 of the locking members 10 in the front part thereof and under said shafts in the rear part thereof are recesses 80 (FIGS. 6, 7, l0) and 81 (FIGS. 6, 7, 11) which periodically communicate through grooves 82 and 83 (FIGS. 7 and 8), made in the face of the rear part 2 of the casing, longitudinal passages 84 and 85 (FIGS. 6 and 7) and vertical passages 86 (FIGS. 7, l0) and 87 (FIGS. 7 and 11) made in the rear part 2 of the casing with the variable volume chambers 12 (FIGS. 3, 4) to ensure radial relief of the locking members 10.

To provide radial relief of the locking members 10, according to the invention, recesses 88 (FIGS. 6, 10) and 89 (FIGS. 6, II) are provided in the front upper part of the locking member 10 and in the rear bottom part thereof, said recesses periodically communicating through a longitudinal passage 90 (FIGS. 6, 8, 10, ll vertical passages 91 (FIGS. 6 and 10) and 92 (FIGS. 6 and 11) with the variable volume chambers 12.

In order to provide axial relief of the locking members 10 by the pressurized working fluid, circular recesses 93 (FIG. 6) are provided on the rear face part of the shafts of the locking members 10, said recesses communicating with the cutouts ll of the locking members 10 through the drilled holes 94 in said shafts and through longitudinal passages 90.

plate 26.

The operation of the rotary-type hydraulic machine as a pump in accordance with the second embodiment thereof is similar to that of the first embodiment, but for several differences, some ofwhich being as follows.

The fluid is sucked in through the hole 72, made in the plate 26 and communicating with the circular space of the hollow member 25.

The fluid is forced from the variable volume chambers 12 through the hole 7K in the front part 1 of the casing, which hole communicates with the circular space 13.

The rotary-type hydraulic machine of the second embodiment, as well as that of the first one, can also be used as a hydraulic motor.

The advantages of the rotary-type hydraulic machine, according to the present invention, are as follows.

The rotor 4, installed on the shaft 3 with a possibility of axial reciprocation, ensures simple and smooth control of the working volume of the chambers 12 within a wide range, which circumstance considerably widens the field of application of the rotary-type hydraulic machine, and also eliminates the fluid pulsation, the rotor radial disbalance and hydromechanical losses during the operation of the rotary-type hydraulic machine with the vanes disengaged.

The design of the rotary-type hydraulic machine, made according to the invention, is simple and allows its use for the operation at high pressure and r.p.m.

Although the present invention is described in connection with a preferable embodiment thereof, it is clear, that various changes and modifications can take place within the spirit and scope of the present invention, as those skilled in the art will easily understand. These variations and changes are to be considered as falling within the spirit and scope of the present invention and the appended claims.

What we claim is:

l. A rotary-type hydraulic machine for the drives of transport vehicles comprising a casing having a front and a rear part, said front part being provided with an internal circular chamber and working fluid passages and said rear part having an internal cylindrical surface provided with longitudinal semicylindrical bores; a shaft installed in said casing; a rotor installed on said shaft having an axial reciprocating motion; said rotor having a cylindrical working part provided with radial vanes having respective longitudinal sides, front and rear hub parts, an internal circular chamber for passing the working fluid, working fluid passages made in the cylindrical working part of said rotor and on one of the longitudinal sides of said vanes communicating with said chamber of the rotor and said working fluid passages also being drilled through the body of said vanes on their other longitudinal side blocked from connection with said circular chamber of the rotor; a control member having through opened semicylindrical bores being installed in the chamber of said casing rear part on the rear hub of the rotor by means of rolling contact bearings; locking members rotating synchronously with said shaft slid having cutouts to endure the motion of said rotor vanes when rotating and performing an axial motion whereby the shafts of said locking members are cantilevered by means of rolling friction hearings in said casing rear part inside said bores of the casing and said bores of the control member, a plate; a hollow member having holes for working fluid and being fixed in side said casing front part on said plate having the working fluid passages and forming a movable liquid sealing with the front hub part of the rotor; a bushing having the internal chamber and longitudinal grooves communicating with said circular chamber in said casing front part to ensure a relative axialmotion of said front hub part of the rotor and its working part with vanes and being installed in the casing front part by means of rolling contact hearings on said hollow member; variable volume chambers formed with the internal surface of said casing rear part, said rotor working part with vanes, said rotatable locking members, said bushing and control member; a means for varying the volume of said chambers by an axial travel of said rotor and control member, said means being formed with the internal surface of the casing rear part, face parts of the rotor and control member and communicating with the working fluid delivery means through a hole drilled in the casing rear part; a screw means to ensure an axial motion of the rotor and control member; and a circular collector having holes for the working fluid inlet and outlet system.

2. A rotary-type hydraulic machine for the drives of transport vehicles comprising a casing having a front and rear part, said front part being provided with an internal circular chamber and working fluid passages and said rear part having an internal cylindrical surface is provided with longitudinal semicylindrical bores; a shaft installed in said casing; a rotor installed on said shaft having an axial reciprocating motion said rotor having a cylindrical working part with radial vanes having respective longitudinal sides, front and rear hub parts, an internal circular chamber for passing the working fluid, working fluid passages made in the cylindrical working part of the rotor and on one of the longitudinal sides of said vanes communicating with said chamber of the rotor and the working fluid passages also being made on the other longitudinal side through the body of said vanes and blocked from connection with said circular chamber of the rotor; a control member having through opened longitudinal semicylindrical bores and being installed in the chamber of said casing rear part of the rotpgrear hubby means of rolling c on ta c t bearings; locking members having respective shafts rotating synchronously with said shaft and having cutouts to ensure the motion of said rotor vanes when rotating and performing an axial motion travel, the locking member shafts being cantilevered by means of plain bearings in said casing rear part in said casing qisiil jl sa or o thersntreLuen saaht low member having a hole drilled to ensure the flow of the working fluid and being fixed inside said casing front part on said plate and having the working fluid passages and forming a movable slot fluid sealing with said front hub part of the rotor; a bushing having the internal chamber and longitudinal grooves communicating with said circular chamber in the front part of said casing to ensure a relative axial motion of said front hub part of the rotor and its working part with vanes and being installed in said casing front part by means of plain bearings on said hollow member; variable volume chambers fofmed with the internal surface of said casing rear part, said rotor working part with vanes, said rotatable locking members, and said bushing and control member; a means for varying the volume of said chambers by an axial travel of said rotor and control member, said means being formed with the internal surface of said casing rear part, face parts of the rotor and control member and communicating through the hole drilled in the casing rear part with the working fluid delivery means; a screw means for an axial travel of said rotor and control member, and a circular collector having the working fluid inlet and outlet system.

3. A rotary-type hydraulic machine as claimed in claim 1, wherein said locking member in said cutout to ensure the motion of the rotor vanes is provided with a hole communicating periodically said variable volume chambers having a clearance between said rear part of the locking member and rolling friction bearing for an axial relief of said locking member by the pressurized working fluid.

4. A rotary-type hydraulic machine as claimed in claim 2, wherein said locking member is provided with a longitudinal passage communicating with the cutout in said locking member through a drilled hole with a circular recess made on the face rear part of the locking member shaft to ensure an axial relief of said locking member by the pressurized working fluid.

5. A rotary-type hydraulic machine as claimed in claim 2, wherein the control member is located under the working parts of said rotatable locking members and is provided with a plurality of crescent-shaped recesses along the length of said cutouts in said locking members, the longitudinal semicylindrical bores of the casing rear part for said locking members in said working part zone are provided with shears of edges along the length of said cutouts in said locking members whereby said shears of edges communicate the locking members periodically with said variable volume chambers to ensure a constant ratio of the working fluid pressures actuating the working part of said locking members when the volume of said chambers is varied.

6. A rotarytype hydraulic machine as claimed in claim 2 wherein the longitudinal semicylindrical bores for said locking members in the casing rear part are located above their respective shafts in their front part and under their respective rear part are provided with recesses; said front face of the casing rear part being provided with grooves, said recesses and grooves communicating and said longitudinal and vertical passages are periodically communicated with said variable volume chambers to ensure a radial relief of said locking members.

7. A rotary-type hydraulic machine as claimed in claim 2, wherein the front top and rear bottom parts of said locking shafts are provided with recesses whose vertical and longitudinal passages made in said locking member shafts communicate periodically with said variable volume chambers to ensure a radial relief of said locking members.

8. A rotary-type hydraulic machine as claimed in claim 1, wherein said control member is provided with a longitudinal passage whereby through face clearance between said rotor and said control member, said variable volume chambers communicate with the circular recesses closed by a thrust flange and made on the rear face part of said control member to ensure an axial relief of said control member by the pressurized working fluid.

9. A rotary-type hydraulic machine as claimed in claim 2, wherein said control member is provided with a longitudinal passage whereby through face clearances between said rotor and said control member said variable volume chambers communicate with a circular recess made on a thrust flange surface in contact with said control member to ensure the axial relief of said control member by the pressurized working fluid.

10. A rotary-type hydraulic machine as claimed in claim 1, wherein the casing rear part along the internal cylindrical surface between said semicylindrical bores for said locking members is provided with recess having a width less than that of said rotor vane and which communicate periodically with said variable volume chambers to ensure a radial relief of said rotor by the pressurized working fluid.

11. A rotary-type hydraulic machine as claimed in claim 2, wherein the casing rear part along the internal cylindrical surface between said semicylindrical bores for said locking members is provided with recesses having width less than that of the rotor vane and which communicate periodically with said variable volume chambers to ensure the radial relief of said rotor by the pressurized working fluid.

12. A rotary-type hydraulic machine as claimed in claim 1, wherein said bushing with grooves to ensure the motion of said rotor vanes has diametrically opposed passages whereby said variable volume chambers communicate additionally with said circular chamber for passing the working fluid in said front part of the casing.

13. A rotary-type hydraulic machine as claimed in claim 2, wherein said bushing with grooves for said rotor vanes had diametrically opposed passages whereby said variable volume chambers communicate additionally with said circular chamber for passing the working fluid in said front part of the casing.

14. A rotary-type hydraulic machine as claimed in claim 1, wherein said bushing with said grooves to ensure the motion of said rotor vanes is provided with a passage whereby through diameter clearance between said casing front part and said bushing, said variable volume chambers communicate with the circular recess made on said plate having the workin fluid passages to compensate for axial hydrostatic forces be ween said rotor and said control member and said bushing.

15. A rotary-type hydraulic machine as claimed in claim 2, wherein said bushing with grooves to ensure the motion of said rotor vanes is provided with a passage whereby said variable volume chambers communicate with a circular recess made on the plate having a hole for passing the working fluid to compensate axial hydrostatic forces between said rotor, said control member and bushing. 

1. A rotary-type hydraulic machine for the drives of transport vehicles comprising a casing having a front and a rear part, said front part being provided with an internal circular chamber and working fluid passages and said rear part having an internal cylindrical surface provided with longitudinal semicylindrical bores; a shaft installed in said casing; a rotor installed on said shaft having an axial reciprocating motion; said rotor having a cylindrical working part provided with radial vanes having respective longitudinal sides, front and rear hub parts, an internal circular chamber for passing the working fluid, working fluid passages made in the cylindrical working part of said rotor and on one of the longitudinal sides of said vanes communicating with said chamber of the rotor and said working fluid passages also being drilled through the body of said vanes on their other longitudinal side blocked from connection with said circular chamber of the rotor; a control member having through opened semicylindrical bores being installed in the chamber of said casing rear part on the rear hub of the rotor by means of rolling friction bearings; locking members rotating synchronously with said shaft and having cutouts to endure the motion of said rotor vanes when rotating and performing an axial motion whereby the shafts of said locking members are cantilevered by means of rolling friction bearings in said casing rear part inside said bores of the casing and said bores of the control member, a plate; a hollow member having holes for working fluid and being fixed inside said casing front part on said plate having the working fluid passages and forming a movable liquid sealing with the front hub part of the rotor; a bushing having the internal chamber and longitudinal grooves communicating with said circular chamber in said casing front part to ensure a relative axial motion of said front hub part of the rotor and its working part with vanes and being installed in the casing front part by means of rolling friction bearings on said hollow member; variable volume chambers formed with the internal surface of said casing rear part, said rotor working part with vanes, said rotatable locking members, said bushing and control member; a means for varying the volume of said chambers by an axial travel of said rotor and control member, said means being formed with the internal surface of the casing rear part, face parts of the rotor and control member and communicating with the working fluid delivery means through a hole drilled in the casing rear part; a screw means to ensure an axial motion of the rotor and control member; and a circular collector having holes for the working fluid inlet and outlet system.
 2. A rotary-type hydraulic machine for the drives of transport vehicles comprising a casing having a front and rear part, said front part being provided with an internal circular chamber and working fluid passages and said rear part having an internal cylindrical surface is provided with longitudinal semicylindrical bores; a shaft installed in said casing; a rotor installed on said shaft having an axial reciprocating motion said rotor having a cylindrical working part with radial vanes having respective longitudinal sides, front and rear hub parts, an internal circular chamber for passing the working fluid, working fluid passages made in the cylindrical working part of the rotor and on one of the longitudinal sides of said vanes communicAting with said chamber of the rotor and the working fluid passages also being made on the other longitudinal side through the body of said vanes and blocked from connection with said circular chamber of the rotor; a control member having through opened longitudinal semicylindrical bores and being installed in the chamber of said casing rear part of the rotor rear hub by means of rolling friction bearings; locking members having respective shafts rotating synchronously with said shaft and having cutouts to ensure the motion of said rotor vanes when rotating and performing an axial motion travel, the locking member shafts being cantilevered by means of rolling friction bearings in said casing rear part in said casing bores and said bores of the control member; a plate; a hollow member having a hole drilled to ensure the flow of the working fluid and being fixed inside said casing front part on said plate and having the working fluid passages and forming a movable slot fluid sealing with said front hub part of the rotor; a bushing having the internal chamber and longitudinal grooves communicating with said circular chamber in the front part of said casing to ensure a relative axial motion of said front hub part of the rotor and its working part with vanes and being installed in said casing front part by means of rolling friction bearings on said hollow member; variable volume chambers formed with the internal surface of said casing rear part, said rotor working part with vanes, said rotatable locking members, and said bushing and control member; a means for varying the volume of said chambers by an axial travel of said rotor and control member, said means being formed with the internal surface of said casing rear part, face parts of the rotor and control member and communicating through the hole drilled in the casing rear part with the working fluid delivery means; a screw means for an axial travel of said rotor and control member, and a circular collector having the working fluid inlet and outlet system.
 3. A rotary-type hydraulic machine as claimed in claim 1, wherein said locking member in said cutout to ensure the motion of the rotor vanes is provided with a hole communicating periodically said variable volume chambers having a clearance between said rear part of the locking member and rolling friction bearing for an axial relief of said locking member by the pressurized working fluid.
 4. A rotary-type hydraulic machine as claimed in claim 2, wherein said locking member is provided with a longitudinal passage communicating with the cutout in said locking member through a drilled hole with a circular recess made on the face rear part of the locking member shaft to ensure an axial relief of said locking member by the pressurized working fluid.
 5. A rotary-type hydraulic machine as claimed in claim 2, wherein the control member is located under the working parts of said rotatable locking members and is provided with a plurality of crescent-shaped recesses along the length of said cutouts in said locking members, the longitudinal semicylindrical bores of the casing rear part for said locking members in said working part zone are provided with shears of edges along the length of said cutouts in said locking members whereby said shears of edges communicate the locking members periodically with said variable volume chambers to ensure a constant ratio of the working fluid pressures actuating the working part of said locking members when the volume of said chambers is varied.
 6. A rotary-type hydraulic machine as claimed in claim 2 wherein the longitudinal semicylindrical bores for said locking members in the casing rear part are located above their respective shafts in their front part and under their respective rear part are provided with recesses; said front face of the casing rear part being provided with grooves, said recesses and grooves communicating and said longitudinal and vertical passages are periodically communicated with said variable volume chambers to ensure a Radial relief of said locking members.
 7. A rotary-type hydraulic machine as claimed in claim 2, wherein the front top and rear bottom parts of said locking shafts are provided with recesses whose vertical and longitudinal passages made in said locking member shafts communicate periodically with said variable volume chambers to ensure a radial relief of said locking members.
 8. A rotary-type hydraulic machine as claimed in claim 1, wherein said control member is provided with a longitudinal passage whereby through face clearance between said rotor and said control member, said variable volume chambers communicate with the circular recesses closed by a thrust flange and made on the rear face part of said control member to ensure an axial relief of said control member by the pressurized working fluid.
 9. A rotary-type hydraulic machine as claimed in claim 2, wherein said control member is provided with a longitudinal passage whereby through face clearances between said rotor and said control member said variable volume chambers communicate with a circular recess made on a thrust flange surface in contact with said control member to ensure the axial relief of said control member by the pressurized working fluid.
 10. A rotary-type hydraulic machine as claimed in claim 1, wherein the casing rear part along the internal cylindrical surface between said semicylindrical bores for said locking members is provided with recess having a width less than that of said rotor vane and which communicate periodically with said variable volume chambers to ensure a radial relief of said rotor by the pressurized working fluid.
 11. A rotary-type hydraulic machine as claimed in claim 2, wherein the casing rear part along the internal cylindrical surface between said semicylindrical bores for said locking members is provided with recesses having width less than that of the rotor vane and which communicate periodically with said variable volume chambers to ensure the radial relief of said rotor by the pressurized working fluid.
 12. A rotary-type hydraulic machine as claimed in claim 1, wherein said bushing with grooves to ensure the motion of said rotor vanes has diametrically opposed passages whereby said variable volume chambers communicate additionally with said circular chamber for passing the working fluid in said front part of the casing.
 13. A rotary-type hydraulic machine as claimed in claim 2, wherein said bushing with grooves for said rotor vanes had diametrically opposed passages whereby said variable volume chambers communicate additionally with said circular chamber for passing the working fluid in said front part of the casing.
 14. A rotary-type hydraulic machine as claimed in claim 1, wherein said bushing with said grooves to ensure the motion of said rotor vanes is provided with a passage whereby through diameter clearance between said casing front part and said bushing, said variable volume chambers communicate with the circular recess made on said plate having the working fluid passages to compensate for axial hydrostatic forces between said rotor and said control member and said bushing.
 15. A rotary-type hydraulic machine as claimed in claim 2, wherein said bushing with grooves to ensure the motion of said rotor vanes is provided with a passage whereby said variable volume chambers communicate with a circular recess made on the plate having a hole for passing the working fluid to compensate axial hydrostatic forces between said rotor, said control member and bushing. 